Trench filling and shoulder spreading machine



Jan. 2, 1962 Filed April 25,

R. D. M DONALD 3,015,261

TRENCH FILLING AND snowman SPREADING MACHINE 1958 13 Sheets-Sheet 1INVENTOR.

I I @yzmi QM Jan 2, 1962 MacDoNALD 3,015,261

TRENCH FILLING AND SHOULDER SPREADING MACHINE Filed April 25, 1958 13Sheets-Sheet 3 a a w 00 & T

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Jan. 2, 1962 R. D. MHC'DONALD 3,015,251

TRENCH FILLING AND SHOULDER SPREADING MACHINE Filed April 25, 1958 13Sheets-Sheet 4 Jan. 2, 1962 R. D. M DONALD 3,015,251

NCH FILLING AND SHOULDER SPREADING MACHINE Fi lllll ril 25, 1958 13Sheets-Sheet 5 Jan. 2, 1962 3,015,261

TREILICH FILLING AND SHOULDER SPREADING MACHINE R. D. M DQNALD l3Sheets-Sheet 6 Filed April 25, 1958 QQ mQ Jan. 2, 1962 R. D. M DONALD3,015,261

TRENCH FILLING AND SHOULDER SPREADING MACHINE l3 Sheets-Sheet 7 FiledApril 25, 1958 Jan. 2, 1962 R. D. M DONALD 3,015,251

TRENCH FILLING AND SHOULDER SPREADING MACHINE 13 Sheets-Sheet 8 FiledApril 25, 1958 Jan. 2, 1962 R. o. M DONALD 3,015,261

TRENCH FILLING AND SHOULDER SPREADING MACHINE Filed April 25, 1958 13Sheets-Sheet 9 INVENTOR.

Jan. 2, 1962 R. D. M DO NALD 3,015,261

TRENCH FILLING AND SHOULDER SPREADING MACHINE Filed April 25, 1958 115Sheets-Sheet 10 INVENTOR.

Jan. 2, 1962 R. D. M DONALD 3,015,251

TRENCH FILLING AND SHOULDER SPREADING MACHINE l3 Sheets-Sheet 11 FiledApril 25, 1958 INVENTOR- Eqynzore D fifczoflarzald, 1M,

Jan. 2, 1962 R. D. M DONALD TRENCH FILLING AND SHOULDER SPREADINGMACHINE 13 Sheets-Sheet 12 Filed April 25, 1958 INVENTOR. ji /more Djiac 507M Jan. 2, 1962 R. D. M DONALD 3,015,261

TRENCH FILLING AND SHOULDER SPREADING MACHINE l3 Sheets-Sheet 13 FiledApril 25, 1958 @marezzmgi BY nrg fi United States Patent C) 3,015,261TRENCH FlLLING AND SHOULDER SPREADING MACHINE Raymore D. MacDonald,Eureka, IlL, assignor to Ulrich Manufacturing (30., Roanoke, 111., acorporation of Delaware Filed Apr. 25, 1958, Ser. No. 730,943 16 Claims.(Cl. 94-46) The present invention relates to that class of roadconstruction machines commonly known as trench'filling and shoulderspreading machines, which are frequently employed in road wideningoperations. In these road widening operations, it is a conventionalpractice to first cut a longitudinal trench out of the soil along oneside edge or margin of an existing road composed of concrete, macadam orother road material, following which this trench is filled withbituminous mix, crushed stone, gravel, concrete or other desired fillingmaterial, such filling operation being performed by a trench fillingmachine. The width of the fill is dependent upon the extent to which itis desired to widen the road, and the depth of the fill is dependentupon the depth of road bed desired, the filling material used, whetherthe new fill and the existing road is to be resurfaced, etc.

Road construction machines of this general type are also employed inshoulder work in which a widened shoulder is spread along the side edgeof an existing road by spreading bituminous mix, crushed stone, etc.along this side edge. In this regard, the present machine hereindisclosed is not limited in use to trench filling operations, but isalso capable of shoulder work in which a widened shoulder is spreadalong the edge of an existing road by spreading black top, crushedstone, etc. to a controlled depth, slope or grade.

One of the principal objects of the invention is to provide an improvedtrench filling and shoulder spreading machine which is constructed inthe form of an attachment unit for quick and easy attachment to anddetachment from a conventional motor grader. The conventional motorgrader thus serves as the prime mover or power vehicle for propelling myimproved attachment unit along the roadway in the trench filling orshoulder spreading operation. Considering the range of equipment ownedby the average road building contractor or road maintenance contractor,the conventional motor grader is generally the primary motorizedvehicle, or is one of the most prevalent pieces of equipment in theentire road working field. Thus, by constructing my improved machine forattachment to a motor grader, I avoid the much greater initial cost andmaintenance cost of a completely self-propelled machine; and I alsoobtain increased productive capacity and other operating advantageswhich stem from the use with the motor grader.

For example, the strike-off blade action of the attachment unit sets upa very large diagonally acting side draft, but the relatively long wheelbase of the motor grader and its great resistance to side drafteffectively resists this side draft set up in the strike-off blade ofthe attachment unit.

According to the improved coupling arrangement herein disclosed, myimproved attachment unit is coupled up to the front end of themotorgrader to be pushed ahead of the grader. Theattachment unit has ahopper at its front end which receives the fill material from successivedump trucks which move into dumping position ahead of the attachmentunit and dump their material from the rear ends of their dumping bodiesinto the hopper. In order that the operation of dumping the materialfrom the dump body of the truck into the hopper of the attachment unitcan be effected without stopping the forward motion of the attachmentunit it is usually necessary to maintain pushing contact between theattachment unit and each dumping truck, whereby the attachment unitpushes the dumping truck ahead of it. Therelatively large traction poweravailable from the motor grader affords sufficient power to push thelargest size of dump truck ahead of the attachment unit in the truckdumping operation, even up the steepest grades.

Another object of the invention is to provide an improved attachmentunit adapted for attachment to a conventional motor grader wherein thestrike-oft blade of the unit is connected to be governed and controlledby the scraper blade of the conventional motor grader. As is well known,the scraper blade of the conventional motor grader is capable of a widevariety of positioning adjustments, such as: (1) raising and lowering ofthe scraper blade; (2) horizontal rotation of the blade around thevertical axis of the blade supporting circle; (3) lateral tilting of theblade by raising and lowering opposite sides of the circle; (4) sideshifting of the blade and blade circle, etc. Most or all of thesepositioning adjustments of the scraper blade are performed by mechanicalor hydraulic power in the later designs of motor graders, and themounting and adjustments of the scraper blade are capable ofwithstanding the extremely large stresses which are encountered by thescraper blade in the ordinary performance of a grading operation by themotor grader. I make these various adjustments of the scraper blade andits sturdiness of mounting available to the strike-off blade of myattachment unit by connecting the outer end of the strike-off blade withthe scraper blade, so that this outer end of the strike-ofi bladeresponds to adjustments given to the scraper blade of the grader. Theinner end of the strike-off blade of my trench filling and shoulderspreading machine is preferably made responsive to a separate andindependent control located on this filling and spreading machine, but,as above stated, the outer end of such strike-off blade is positivelyconnected with and made responsive to the scraper blade of the grader.Thus, it Will be seen that by making the outer end of the strike-0Eblade of 'my machine responsive to positioning adjustments of thescraper blade of the motor grader, I can efiect all of the necessarypower operated adjustments of the outer end of the strike-ofii blade,through the motor grader, without burdening the attachment unit with thesubstantial cost, complication and weight of providing such poweroperated adjustments on the attachment unit. Still further, as aboveintimated, I utilize the very large side draft resistance inherent inthe motor grader to sustain the side draft set up in the outer end ofthe strike-oil? blade of my attachment machine. In this regard, theabove described feature of pushing the attachment unit ahead of themotor grader constitutes a very important factor in being able toestablish the desired adjusting and side draft transmitting connectionbetween the scraper blade of the motor grader and the strike-01f bladeof the attachment unit, whereby the outer end of the strike-off blade ismade responsive to controls effected through the scraper blade, and alsohas its side draft borne by the scraper blade.

Another object of the invention is to provide an improved three-pointmounting or suspension of the attachment unit. These three pointscomprise two laterally spaced caster wheel sets at the front of theattachment unit, and'a ball-and-socket mounting joint between the rearportion of the attachment unit'and the front end of the motor grader.This three point mounting of the attachment unit, with the universaljoint type of draft transmitting connection between the attachment unitand the motor grader, permits relative transverse rocking movementbetween the attachment unit and the motor grader,

each independently of theother, as the two vehicles pass over unevenroad surfaces. A pivotally acting stabilizer brace extends between themotor grader and the attachment unit, preferably having aball-and-socket connection at its front end with the attachment unit.This stabilizer brace compels the attachment unit to steer directly withthe front end of the motor grader, and supplements the drafttransmitting action of the ball-and-socket mounting joint, while stillpermitting the free transverse rocking movement between the attachmentunit and motor grader. This free tranverse rocking movement results inthe strike-off blade being more accurately maintained at itspredetermined set height of strike-off of the filling material, as willbe later described. This free transverse rocking movement also avoidsthe transmission of twisting, racking stresses from the frame of themotor grader to the. frame of the attachment unit, or vice versa.

Another object of the invention is to provide an improved lifting jack,preferably hydraulic in its operation, for manually lifting and loweringthe rear end of the attachment unit in performing the manual operationof coupling and uncoupling the attachment unit and the motor grader atthe ball-and-socket mounting joint.

The trench filling and shoulder spreading unit has "a conveyor belttraveling in the bottom of the material receiving hopper of the unit fordischarging this material along the side edge of the road; and anotherobject of the invention is to provide improved regulating means forregulating the speed of travel of this conveyor belt through infinitelysmall speed changes. Thus, it is possible for the operator to regulatevery closely the rate of discharge of the. filling material to take careof different depths and widths of fill and different operatingconditions.

Another object of the invention is'to provide an improved hydraulicallytilted dump apron or front hopper wall at the front edge of the materialreceiving hopper, which can be readily raised and lowered by theoperator for the purpose of accommodating different body heights ofdifferent dump trucks, and also for the purpose of increasing the hoppercapacity. This tiltable dump apron increases the capacity of the hopperby providing a front hopper wall which can be disposed substantiallyhorizontally for receiving material during the truck dumping operation,and which can thereafter be tilted upwardly to discharge the materialresting thereon rearwardly back to the conveyor belt.

' Another object is to provide an improved design of hinged trench andcurb seal which will prevent material from being carried from the trenchback under the rna chine on to thepavement; and which can also bereadily folded up out of the trench when the machine is in transport.

Further objects of the invention pertaining to the conveyor belt of themachine are to provide improved selfcleaning conveyor belt seals whichare tapered so as to be self-relieving in the direction of travel; toprovide an improved floating type of inside belt scraper at the tailpulley of the belt; and to provide an improved arrangement of clean-outholes in the sides of the conveyor belt channel.

. Still another object is to provide the machine with an improved frameconstruction characterized by a trans versely'extending frame tube whichfunctions firstly as the backbone of the frame; secondly it serves as anoil reservoir adapted to store a large quantity of oil for the hydraulicdrive' and control systems; and thirdly because 7 front portion of aconventional motor grader and showing the trench filling embodiment ofmy improved attachment unit coupled thereto, this trench fillingembodiment being designated AU.

FIGURE 13 is a similar view showing the shoulder spreading embodiment ofthe attached front unit, coupled to the conventional motor grader, thisshoulder spreading embodiment being designated AU.

FIGURE 2 is a perspective view of the rear end of the attachment unithaving the trench filling equipment mounted thereon, showing ituncoupled from the motor grader.

FIGURE 3 is a fragmentary rear elevational view of most of one of theattachment units, showing it uncoupled from the motor grader similarlyto FIGURE 2.

FIGURE 4 is a fragmentary perspective view of the left hand portion ofthe trench filling embodiment of attachment unit AU, showing the frontand left hand side thereof.

FIGURE 5 is a side elevational view of the trench filling embodiment AU,showing the strike-'ofi box in its lowered position in a trench.

FIGURE 6 is a somewhat similar view of this same trench fillingembodiment, AU on a slightly smaller scale, with the strike-01f boxremoved or broken away to illustrate more clearly the point of dischargeof the fill ma terial from the machine, this view also illustratingfragmentarily the rear end of a dump truck in the act of dumping fillmaterial into the hopper.

FIGURE 6A is a view quite similar to FIGURE 6, but of the shoulderspreading embodiment AU.

FIGURE 7 is an isolated fragmentary plan view of the stabilizer barwhich is connected between either of the two attachment units AU, AU,and the motor grader.

FIGURE 8 is a plan view of an'irnproved floating type of inside beltscraper used on either embodiment AU or AU, this view being on alargerscale.

FIGURE 9 is afragmentary elevational view of my improved design ofhinged trench and curb seal used on either embodiment.

FIGURE 10 is a transverse sectional view through the same, takenapproximately on the plane of the line 10- 10 of FIGURE 9.

FIGURE 11 is a detail section taken on the plane of the line 11-.11 ofFIGURE 5.

FIGURE 12 is a fragmentary side elevational view of the intermediateportion of the conventional motor grader MG illustrated in FIGURES 1Aand 1B, but on a' larger scale, and FIGURE 13 is a fragmentarytransverse sectional view taken on the plane of the line 13-43 of FIG-URE 12, these two figures showing in greater detail certain of theconventional controls ordinarily utilized for efiecting lifting,lowering and lateral shifting adjusting movements of the conventionalscraper blade of such a grader, which adjusting movements aretransmitted from such scraper blade to the strike-off blade' of theshoulder spreading attachment unit AU of FIGURE 1A.

' FIGURE 14 is a' fragmentary elevational view of part 'of said shoulderspreading attachment unit AU, corresponding to a section takenapproximately on the plane of the line 14- 14 of FIGURE 1A, showing thevertically moving hydraulically operated slide, together with theflinging articulation and pivoting articulation of the inner end of thestrike-off blade of said shoulder spreading attachment unit AU.

FIGURE 15 is a fragmentary plan view of FIGURE 14. FIGURE 15A is adetail section of FIGUREIS. FIGURE 16 is a fragmentary elevational view,corresponding to a view taken on the plane of the line 1616 of FIGURE1B, showing the extensible boom for connecting the scraper blade ofjthemotor grader with the strike-01f blade of the shoulder spreadingattachment unit AU.

FIGURE 17 is a fragmentary plan view of FIGURE 16. FIGURE 18 is afragmentary elevational view, corresponding to a view taken on the planeof the line 18. 13

of FIGURE 1B, showing the margin defining plate and the shoe plate atthe outer end of the strike-off blade.

FIGURE 19 is a plan view of FIGURE -18.

FIGURE 20 is a fragmentary detail view showing in vertical section theball and socket transversely rockable mounting joint which couples therear portion of the attachment unit to the front end of the motorgrader, and;

FIGURE 21 is a transverse detail sectional view taken approximately onthe plane of the line 21-21 of FIG- URE 20.

In FIGURE 1A I have shown the trench filling embodiment of my attachmentunit, designated AU in its entirety, and in FIGURE 13 I have shown theshoulder spreading embodiment of my attachment unit, designated AU inits entirety. Both attachment units are quite similar up to the point ofdischarge of the fill material from the conveyor belt, following whichthe trench filling embodiment causes the fill material to fill apreviously cut trench along the side of the road, whereas the shoulderspreading embodiment causes the fill material to be spread outwardlyfrom the side of the road, usually over a substantial span, to build upthe shoulder along side the road. Both attachment units are to becoupled to the front end of any conventional or standard motor grader,which is designated MG in its entirety. The attachment unit AU or AU isadapted to receive its filling material from successive dump truckswhich are pushed ahead of the attachment unit and which dump rearwardlyinto the material receiving hopper of the unit, the rear end of one ofsuch dump trucks being indicated fragmentarily at DT in FIGURE 6.

Because of the close collaboration of the motor grader MG with each ofthe attachment units AU, AU I shall first briefly describe the mainparts of a conventional motor grader. It usually comprises a suitableframe structure 25 supported at its front end on front steering wheels26 and at its rear end on rear driving wheels 27. The rear drivingwheels are generally but not necessarily in tandem pairs. An internalcombustion engine 29 operates to drive the rear driving wheels 27 andalso the accessories, such as the oil pump of the hydraulic controlsystem; and in the case of a six wheel drive motor grader this enginealso serves to drive the front steering wheels 26. Located under theframe 25 between the front wheels 26 and rear wheels 27 is theconventional scraper blade 36 which is so mounted and connected with theframe 25 as to be capable of a wide variety of positioning adjustments.For example, the blade is mounted on a so-called circle 31 having asubstantially vertical rotative axis which enables the scraper blade tobe rotated in a substantially horizontal plane to different horizontalangles under the frame 25. The horizontal rotation of the blade aroundthe axis of the circle 31 is usually performed by an engine drive into agear box, as is well known. The scraper blade 30 and circle 31 are alsocapable of a sideshifting adjustment, usually performed by theenergization of hydraulic rams or mechanical linkage in a well knownmanner, so as to enable either end of the scraper blade 30 to beprojected out to a greater or lesser distance to each side of the frame25. Moreover, the circle 31 can be tilted around a fore and aft axisextending substantially longitudinally of the grader, as by theenergization of hydraulic rams or mechanical drive, in a well knownmanner, so that either side of the circle can be tilted up- .wardly ordownwardly, whereby the corresponding end of the scraper blade can alsobe tilted upwardly or downwardly as desired. Still further, the entireassembly of the circle and blade can be raised and lowered to vary thecutting depth of the blade, and to swing the blade up to a raisedinoperative position, as by the operation of the hydraulic rams ormechanical linkage, as is well known. In the later designs of motorgraders, all of these blade positioning adjustments are effected in re--sponse to the operation of control levers or the like 36 located at theoperator's position 37 on the motor grader.

These lifting, lowering, tilting and side shifting adjustments of thescraper blade 30 of the motor grader are utilized in effectingadjustments of the outer end of the strike-off blade of the shoulderspreading attachment unit AU, and will be described in greater detaillater, preliminary to the description of this shoulder spreadingattachment unit. Both embodiments of attachment units AU and AU havepreferably been constructed and proportioned for use particularly inconjunction with six wheel motor graders having tandem pairs of reardriving wheels 27 and having front steering wheels 26 which may or maynot be power driven, and the same or a comparable grader is illustratedin the drawings, but it will of course be understood that the inventionis not limited to use with either of these specific graders.

Referring now to the main features forming the structural basis of bothembodiments AU and AU, and with particular reference first to FIGURES 2,3, 5, 6 and 7, it will be seen that the main frame thereof is of torquetube and box section design comprising at the rear a transverselyextending horizontal tank tube '40 which constitutes the main back-boneof the frame. This tank tube 40 functions as an oil reservoir forstoring a reserve quantity of oil for the hydraulic drive and hydrauliccontrol system, and in this regard the large surface area of such tanktube functions effectively to dissipate the heat from the circulatingoil. The ends of the tank tube 40 are closed by removable end heads 41,the removal of which affords access to the interior of the tank tube forcleaning the latter.

Welded to the underside of the tank tube 40 substantially at its centeris the downwardly extending mounting bracket 43 having a sphericalsocket 44 formed in its underside. Secured to and projecting from thefront end of the motor grader MG is an upwardly extending ball 45 whichis adapted to establish a ball-andsocket mounting joint within thespherical socket 44. A removable cap 46 having a spherical pocket in itsupper surface is detachably secured by belts or cap screws 47 to theunderside of the mounting bracket 43. This ball and socket mountingjoint 44, 45, the details of which are best shown in FIGURES 20 and 21,constitutes the main draft transmitting connection between the motorgrader MG and the attachment unit AU, and it will be seen that by themere removal of the bolts or cap screws 47 this draft transmittingconnection can be easily separated for uncoupling the attachment unitfrom the motor grader. The shank of the mounting ball 45 is welded to across plate 49 which in turn has its ends welded to a pair of laterallyspaced links 51 extending upwardly and rearwardly therefrom. The rearends of these pivoting links 51 engage over opposite ends of atransversely extending boss 52 formed integral with the front end of themotor grader frame, and a transverse pivot pin 53 passes through thepivoting links 51 and boss 52. Welded to the underside of the plate 49and extending downwardly therefrom is a pair of laterally spaced arms 55having a transversely extending plate 56 welded to their lower ends andprojecting laterally beyond the arms. A U-shaped clevis 57 has itsspaced ends passing through loose fitting holes in the projecting endportions of the plate 56, and nuts 58 screw over threads on the ends ofthe clevis. The clevis 57 embraces a curved arm or web 61 formedintegral with the front end of the motor grader frame. By loosening thenuts 58 the clevis 57 may be shifted upwardly or downwardly along thecurved arm 61 for raising or lowering the mounting height of the ball 45with respect to the front end of the motor grader frame. If desired, anadjusting screw 62 may be threaded through a tapped hole in the plate 56between the spaced arms 55, by the adjustment of which screw the rearsurface of plate 56 can be adjusted toward or away from the curved frontsurface of the arcuate web 61, thereby raising or lowering the height ofthe ball 45.

'The frame of the attachment unit AU also comprises ing transverse pivotpins or axles 69 on which one or more caster wheels 70 are mounted. Thetwo laterally spaced caster wheel sets 70, 70 constitute two spacedpoints of support for the front end of the attachment unit frame,

and the ball-and-socket mounting joint 44, 45 constitutes a thirdlaterally rockable point of support for the rear end of the attachmentunit frame. It will be evident that the ball-and-socket mounting joint44, 45 permits independent transverse rocking movement between the motorgrader MG and the attachment unit AU as the two vehicles pass overuneven road surfaces. I have found it preferable to use solid rubbertires on the caster wheels 70 so as to avoid the rise and fall of thestrike-off blade level to which pneumatic tires are subject withdifferent loads in the.

hopper. The solid rubber tires also enable single caster wheels to beused in many instances, as shown in FIG- URE 4, instead of pairs.

Extending between the right hand side of each of the attachment units AUand AU and a rearwardly disposed point of themotor grader MG is apivotally acting stabilizer brace 72, which compels the attachment unitto steer directly with the front end of the motor grader (as permittedby the castering action of the wheels 70) and which also supplements thedraft transmitting action of the ball-and-socket mounting joint 44, 45,while still per mitting the aforesaid free transverse rocking movementbetween the attachment unit and the motor grader. As shown in FIGURE 7,this stabilizer brace 72 is preferably in the form of a long tube havinga readily releasable bal'-and-socketconnection at its front end with theright hand end of the tank tube 40. This ball-and-socket connectioncomprises front and rear halves 74 and 75 of a spherical socket 76adapted to engage over a ball 77 which projectsupwardly from the righthand end of the tank tube 40. The rear socket half 75 is secured to thefront end of the stabilizer tube 72, and the front socket half 74 isreleasably secured to the rear socket half-over the, ball 77-by two ormore bolts or cap screws 78. This permits the ready disconnection of thestabilizer brace 72 when the attachment unit is to be uncoupled from theURES 1A, 1B and 3 that the single point axis of this ball and socketjoint lies in the longitudinal central vertical plane passing throughboth the motor grader MG and the, attachment .unit AU. or AU; asindicated by the dash-dot lines P-P in FiGURES 1A and 1B. This plane P-Ppasses midway in the tread spans of all. four pairs of wheels, namelythe two pairs ofrear driving wheels 27-27 of the motor grader MG, thepair of front steering wheels 26-26 of the motor grader, and the frontcaster wheels 70-70 of the attachment unit AU or AU. The freedom of thetwo vehicles MG and AU-AU' to have this relative transverse rockingmovementis not hindered in any sense by the presence of thelong'diagonal stabilizing bar 72, the opposite ends of'this stabilizerbar merely rising or falling relatively to each other in accommodatingopposite directions of relative transverse rocking movement between thetwo vehicles. If desired, a duplicate stabilizing bar 72'may be arrangedon the other side of 3 the longitudinal -plane"P-P, comparable toa'wish-bone relation, but I find that a single stabilizing barisentirely adequate. As previously described, this stabilizing barcompels the attachment unit to steer. directly with the front end of themotor grader, as permitted by the castering action of the frontattachment unit wheels 70; and the stabilizing bar also supplements thedraft transmitting action of the ball and socket mounting joint 44-45,while still permitting the aforesaid free transverse rockingmovementbetween the two vehicles around a longitudinal axis lying in the centralvertical plane PP. Such freedom of the two vehicles to have thisrelative transverse rocking movement therebetween results in thestrike-off box 175 or the strike-off blade 275 (to be later described)being more accurately maintained at its respective predetermined heightof strike-off of the filling material, irrespective of any pronouncedundulations in the road surface encountered by the vehicle wheels 27, 26or 70. For example, if the left hand rear traction wheels 27 of themotor grader MG should drop into a hole or depression along the lefthand edge of the road, or should drop off this edge of the road, thiswould immediately tend to cock or twist the grader frame to bring theleft hand side of the entire length of the frame down to a lower levelthan the right hand side. Let us assume that the attachment unit AU-AU'was coupled to the motor grader MG in some such coupled relation thatthe free, transverse rocking movement afforded by the transverselyrockable joint 44-45 could not occur, then there would be a tendency totransmit the entire cocking or twisting of the grader frame to the frameof the attachment unit AU. This could very well tend to depress theinner side or inner end of the laterally projecting strike-off box orstrike-off blade through a substantial degree of downward movement belowthe predetermined set strike-off level, with the result that asubstantially lesser depth of material wouldrbe laid along this part ofthe road. This downward stressing of the strike-off side might beaugmented at times by the overhanging weight of a long length ofoutwardly extending strike-off blade.

Now let us assume the present situation wherein the two vehicle framesare connected together by the cenrally aligned transversely rockablejoint 44-45. In such a situation no part of the transverse cocking ortwisting which is acting through the grader frame can be transmitted tothe attachment unit frame; Also, only one-half of the downward verticalcomponent caused in the left hand side of the grade frame, by the lefthand rear grader wheels dropping into a hole, will be transmitted as adownward component to the rear edge of the attachment unit tending toswing this edge of the attachment unit downwardly around the frontcaster wheels 70-70. The transmission of this downward'component fromthe grader frame to the attachment unit frame is reduced to'one-half 'byreason of the fact that the transversely rockable joint 44-45 onlytransmits to the attachment unit frame onehalf of the downward componentoccurring in the grader frame because the line of action of thetransversely rockable joint 4445 lies in the central plane P-P, which isexactly one-half or is midway of the distance between each pair ofcompanion wheels. Thus, in the present instanceunder discussion, theattachment unit frame receives no twisting stress, and the inner side orinner end of the strike-off box or blade is only depressed one-half asfar as in the other instance where there is no transversely rockablejoint between the two vehicle frames.

This would also be true in the reverse situation of the right'hand reartraction wheels 27 dropping into a hole or depression on their side ofthe road.

' It will also be seen from the foregoing that the abovedescribed actionof the transversely rockable joint 44-45 in avoiding the transmission oftwisting stresses from one vehicle to the other, also avoids thetransmission of racking and twisting stresses from the frameof theattachment unit to the frame of the motor grader or other propellingvehicle. These racking,.twisting stresses are very likely to occur whenthis shoulder spreading or two vehicle assembly is in transport,traveling at speeds ranging up to 20 miles per hour or more, and overconsiderable distances; or when the two vehicles are passing overbridges, around culverts, or driving over irregular ground. Also, thesestresses are almost bound to occur when turning the two vehicle assemblyaround at the end of a shoulder-spreading run or pass along one edge ofa road, possibly for making another shoulder-spreading run back in theopposite direction along the opposite side of the road, this operationof turning around almost inevitably occurring over some rough ground inview of the fact that the overall length of the shoulder spreadingvehicle assembly is in the neighborhood of 30 feet. While the fore andaft axis of the single point transversely rockable balland-socket joint44-45 preferably lies on the central longitudinal plane PP of the twovehicles (FIGURES 1A, 1B), for obtaining the maximum benefits andadvantages pointed out above, nevertheless this fore-and-aft axis ofthis transversely rockable joint 4445 might not be centrally disposed onthe central plane P-P, but might be offset therefrom toward either theright or left wheel lines of the two vehicles, possibly with somesacrifice of certain of the aforementioned benefits and advantages. Thestabilizing bar 72 would continue to be used with any such offsetlocation of the transversely rockable draft transmitting joint.

When the attachment unit AU or AU is uncoupled from the motor grader bythe separation of the balland-socket mounting joint 44, 45, and thedisconnection of the stabilizer brace 72, the weight of the rear end ofthe attachment unit is brought to bear on a jack roller or wheel 82which is lowered into engagement with the road surface for taking thisweight of the rear end of the attachment unit AU or AU off of theball-and-socket mounting 44, 45 to facilitate disconnection of suchmounting; and this rear roller 82 may also be employed to support therear end of the attachment unit in 21 normal or raised position whilethe attachment unit is standing idle, disconnected from the motor graderMG. While these are the preferred utilities of this rear roller 82, itmay also be employed to support substantially all or part of the weightof the rear end of the attachment unit AU or AU while the latter isbeing propelled forwardly in the trench filling or shoulder spreadingoperation, as I shall presently describe. This jack roller 82 is pivotedat 83 between the side arms of a mounting clevis 84 which is secured tothe rear end of a vertically swinging arm or yoke frame 85. The frontend of the arm or yoke frame 85 has wide-axis mounting on a pivot pin orpins 86 supported in pivot lugs 87 projecting from the trench fillerframe. Welded to the underside of the tank tube 49 and extendingdownwardly therefrom is a rigid jack leg 91 having a clevis shaped lowerend 92 carrying a transverse pivot pin 93. Pivoted on the pin 93 is apivot block 94 at the upper end of a piston rod 95 which extendsdownwardly into the cylinder 96 of a one way or single action hydraulicjack 97. Projecting from the lower end of the cylinder 96 is a pivotblock 98 which is mounted on a transverse pivot pin 99 extending throughthe upper portion of the clevis 84. One or more return springs 100 areconnected between the clevis 84 and the upper portion of the frame fornormally holding the jack roller or wheel 82 elevated. When theattachment unit is in its coupled relation to the motor grader MG, withthe mounting ball 45 seating in the mounting socket 44, the jack rolleror wheel 82 may be held in an elevated position out of contact with theroad surface by the action of the tension springs 100, unless it isdesired that this rear roller 82 sustain part of the weight of the rearend of the attachment unit AU while the latter is in operation in atrench filling or in a shoulder spreading operation. When it is desiredto uncouple the attachment unit AU or AU from the motor grader,hydraulic pressure is caused to act in the hydraulic jack 97 for forcingthe jack roller 82 downwardly against the roadsurface, thereby elevatingthe rear end of the attachment unit frame and enabling the mountingsocket 44 to be easily lifted off of the mounting ball 45. The rear endof the attachment unit frame may be maintained in this elevated positionby the hydraulic jack 97 during the entire time that it is uncoupledfrom the motor grader, or the rear end of the attachment unit frame maybe lowered for resting on a suitable support other than thehydraulically maintained position of the jack roller 82. A small handoperated hydraulic pump 101 is mounted adjacent to the hydraulic jack 97and is hydraulically connected therewith, so that the rear end of theattachment unit can be raised and lowered by the hand operation of themanually operated pump 101 and its conventional relief valve. When it isdesired to have this roller 82 carry part or all of the weight of therear end of the attachment unit AU during the trench filling or shoulderspreading operation, the hydraulic pump 101 is manually operated toforce the roller down against the road surface with sufiicient pressureto support any desired proportion of the weight of the rear end of theattachment unit AU, the hydraulic characteristics of the jack 97 lockingthe wheel 82 in this lowered rolling position. Because of the fact thatit is only a single wheel and because of its location quite close to thefore and aft center line of the attachment unit AU, well between thefront steering wheels 26-26 of the motor grader MG, it follows that thissupporting roller or wheel 82 will track or follow sufficiently wellduring any of the steering movements of the motor grader and attachmentunit, which are always on a large radius owing to the long wheel base ofthe combined vehicles.

Located between the tranversely extending rear and front frame tubes 40and 65 a material receiving hopper 105 into which is dumped the hot orcold asphaltic mix, crushed rock, gravel or other material used inmaking the trench fill. This hopper comprises side walls 106, 106', asloping rear wall 107, and a hydraulically operated vertically swingingdump apron or front hopper wall 108 (FIGURE 6) at the front edge of thehopper. This hydraulically operated dump apron or wall 108 comprises atransversely extending plate or wall 109 extending substantially fromside wall to side wall of the hopper, and having a hinged rear edgewhich is pivotally mounted on a transversely extending pivot rod 111secured to the frame. The front edge of the plate 109 is formed with anupwardly bent lip 112 to which is secured an upwardly extending sectionof pliable belting or webbing 113 adapted to strike the underside of thedump truck body. Projecting downwardly from the underside of the apronplate 109 substantially at its center are spaced pivot brackets orplates 115 carrying a pivot pin 116 therebetween, on which is pivoted aneye or clevis 117 secured to the upper end of a piston rod 118. Thispiston rod extends into a double acting hydraulic cylinder 119 which arepivotally connected at 120 at its lower end to the frame of the machine.This front hopper wall 108 normally occupies the relatively fiatposition shown in full lines in FIGURE 6. In the truck dumpingoperation, this front hopper wall 108 can, if desired, be swung upwardlyby energizing the hydraulic ram 119 to bring the pliable upper edge 113into engagement against the underside of the dumping truck body whilethe latter is tilting rearwardly in the performance of the dumpingoperation. In this manner, the fill material is prevented from spillingforwardly between-the under side of the truck body and the hopper 105,irrespective ofwhether it is a high dump truck or a lowone. After thedump truck has pulled away this front hopper wall 108 is given an upwardtilting movement for dumping all of the material which has been dumpedthereon by the truck, this rriaterial being carried up to an angleconsiderably beyond the angle of repose for discharge rearwardly towardthe conveyor belt. It will thus be seen that the tiltableapron or WaJl10 8, in its normal forwardly extending position, considerably increasesthe effective capacity of the hopper. Also, by

virtue of the hydraulic cylinder operation of the filtable apron 168 itcan be utilized to release or free sticky blacktop or like materialwhich may tend to adhere within'the body of the dump truck even afterthe truck body has been raised to its maximum angle of tilt. This loadreleasing operation is performed by suddenly admitting full hydraulicpressure to the ram 119 for causing the apron 108 to swing up with aquick motion so as to strike the underside of the tilted truck body witha sharp blow; or it may be performed by causing the apron to slowly liftthe entire truck body when in its til-ted position, and to then sharplydrop the'truck body to shake the load loose. Material adhering to thehydraulically operated apron 108 may also be shaken loose by quicklyoperating the hydraulic ram 119 in opposite directions, with the motionsuddenly interrupted in each direction by the piston of the ram 119striking the opposite ends of the ram cylinder, or the gate strikingopposite end stops.

Rotatably mounted at the front edge of the machine are two horizontallydisposed pusher rollers 122 122, whichare adapted to engage the rearwheels 123 of the dump truck for pushing the dump truck DT ahead of theattachment unit. AU or AU while the dump truck is dumping fill materialinto the hopper 105 during continuous forward movement of the attachmentunit. These two rollers 122 are spaced apart a distance corresponding tothe tread span of the rear wheels of the conventional dump truck. Inregard to tread span, it should be noted that the tread span between thetwo caster wheel sets 70, 70 is substantially the same as the tread spanof the motor grader wheels 26 and 27, thereby facilitating the loadingof'the attachment unit AU or AU on to a heavy duty transport trailer andthe detachment of the motor grader therefrom when it is desired totransport the attachment unit a substantial distance.

The rear hopper wall 107 and. the hydraulically operated front hopperwall 108 discharge the material downwardly into a transversely extendingfeed channel 131 in the bottom of which travels a conveyor belt 132.Anchored along the front and rear side walls of the feed channel 131 aredownwardly inclined deflecting plates 133, and secured to the undersidesthereof are pliable sealing strips 134 composed of belting or rubberflashing material which establish sealing contact with the upper surfaceof'the conveyor belt 132. The deflecting plates 133 and theself-cleaning pliable sealing strips 134 are tapered in width or havetheir edges extending in diverging relation in the direction of travelof the belt, so that they are self-relieving of fil-l material as thematerial is carried toward the discharge end of the belt at the lefthand side of the machine.

As shown in FIGURE 3, the right hand end of the corrveyor belt 132passes around an adjustable idler roller 136 which is located at theright hand side of the machine. The shaft 137 of this idler roller ismounted at its ends in bearing blocks 138 which are capable ofadjustable sliding travel along guideways 139. Adjusting screws 141threading through yoke bars 142 effect sliding adjustment of the bearingblocks 133 for adjusting the tension on the conveyor belt 132. The toprun of the belt carries a substantial part of the weight of the fillmaterial in the hopper 105, and, accordingly, this top run is supportedat Q closely spaced intervals by supporting rollersn144 carried 1' bythe frame andextending fore and aft directly below fiho top'run of thebelt. At its left hand end (FIGURE 7 a I 3) the conveyor belt passesaround a driving roller 1 47 which is also pivotally mounted in slidable bearing blocks 149, whereby the axis of this driving roller 147mayalso 7 belt.

through a speed reducer of approximately a 20 to 1 ratio with thedriving pulley 147. The hydraulic motor 154 is'adapted to be driven froma hydraulic pump 157 which, in turn, is driven by a gasoline engine 158.One such hydrauliepump which has proven entirely satisfactory for thepurpose is a well known gear pump having multiple pumping compartments.The internal combustion engine 158, hydraulic pump 157 and hydraulicmotor 154 are extended in line along the rear edge of the machine,substantially entirely beneath the upwardly and rearwardly sloping rearhopper wall 107. However, in the use of certain designs of internalcombustion engines, the projection of a part of the engine above theplane of this inclined rear hopper wall 107 may necessitate forming anupwardly bulged formation 107a in this rear hopper wall in the immediatevicinity ofthe engine.

The operator of the trench filling attachment unit AU sits on atransversely facing seat 161 which is located at the left hand side ofthe machine directly over the trench to be filled and immediatelyadjacent to the large discharge opening 162 in the hopper sidewall 106,through which the conveyor belt 132 discharges the fill material. Theseat is mounted on a tubular bracket 163 projecting laterally from theside of the machine frame. Directly in front of the operators seat 161are located controls 164166, one of which controls in a continuously oruniformly graduated manner the flow of hydraulic pressure to thehydraulic motor 154. Thus, it is possible for the operator to regulatewith infinitely small speed changes the rate of discharge of the fillingmaterial from the discharge end of the conveyor belt 132 in order totake care of different depths and widths of fill and different operatingconditions.

Referring to FIGURES 3 and 6, it will be seen that there is provided aplurality of spaced clean-out holes 167 in the vertical front and rearwalls 131 of the feed channel. These clean-out holes afford access toboth edge portions of the top run of the conveyor belt 132 that projectoutwardly beyond the sealing strips 134, and also to the top surface ofthe lower run of the belt. These clean-out holes are particularly usefulfor introducing live steam, furnace oil etc. for cleaning outencrustations of hot or cold asphaltic mix or other foreign matter; andalso assist in discharging foreign matter in the normal running of thebelt. To further aid in the cleaning of the conveyor belt 132, it willbe seen from FIGURE 3 that the bottom return run of the belt is causedto pass upwardly over a centrally located idler roller 168, therebyaiding in the gravitational discharge of dirt and other foreign materialfrom the bottom run of the belt. Still further, it will be seen fromFIGURES 3 and. 8 that I have provided/a unique design of floating insidebelt scraper 169 adjacent to the tail pulley 136. This inside beltscraper is of V-shaped outline comprising spaced bars 170a and'170bbent-to define sloping side wings 170, and having strips of pliableflashing material 170c clamped between the bars 179a and 17%. The loweredges of the pliable flashing material project below the bars forhearing against the top side of the return run of the belt, The V-shapedrelationship of Wings 170 is pivotally connected at 171 to verticallyswinging draft links 172 which are pivotally connected at their otherends to a pivot pin 173 carried by a stationary bracket 174 extendingdownwardly from the frame structure between the upper and lower runs ofthe The pivoted linkage support of the V-shaped scraper 169 enables ittohave floating movement so that be ghifigd inwardly 0r Outward y themanipulation 0f it rides in directxgravitational contact against the top'adjusting'screws" 151, to provide proper" belt alignment.

' The left hand driving roller 147 is driven through suitable drivinggearing (notshown) from a hydraulic; motor 15 whichiispreferably-a'vauetype of hydraulic motor. One such hydraulic motor which hasproven'sab 7 isfactor'y for. the purpose isa relatively small high speedwane. motor, of well known make, which. is connected side. of the returnrun of the belt, before this returnrun passes under the tail 'pulley137. It will'be'obvious that the V'-shaped deflecting wings 179 willdeflect dirt and other foreign matter in an outward direction from thetop side of the return run of the belt. The above described features ofthe clea'n-out'boles; sealing strips, V-shaped belt scraper, etc., arepresent in both attachment'unit embodiments AU and AU.

Referring now more particularly to the trench filling embodiment AU, andto the manner of effecting the strike-oif control of the material as itis discharged from the end of the conveyor belt down into the trench orshoulder area along the edge of the road, in one embodi ment of theinvention this is effected by a strike-off box 175 which is detachablymounted on the left hand side of the machine for vertical adjustingmovement. Referring particularly to FIGURES 4 and 5, the strike-off box175 is a two-sided structure which can be pivotally raised and loweredby the operation of a double acting hydraulic ram 176 for effectingdifferent levels of strike-off of the fill material. The box can also bevaried in width for obtaining different widths of fill. The boxcomprises a back wall 177 and an outer wall 178 which are adapted to beswung up and down together by the hydraulic ram 176 around the pivotaxis x of a rotatable extension tube 180 that telescopes within thefront frame tube 65. As shown in FIGURE 4, the extension tube 180 has aplurality of spaced arcuate slots 181 in its top surface, into which isprojected a retractable latching pin 182 which is slidably mounted in aboss 183 carried by the frame tube 65. The withdrawal of the locking pin182 permits the extension tube 180 to be slid inwardly or outwardlywithin the frame tube 65 for bringing any desired one of the arcuateslots 181 into registering position to receive the latching pin 182,depending upon the desired strike-off width of the box 175. The arcuateformation of each of the slots 181 permits the slight rotative movementof the extension tube 180 within the frame tube 65, which occurs whenthe strike-off level of the box 175 is raised or lowered.

The outer wall 178 of the strike-off box comprises a triangular plate185 having its apex welded or otherwise secured to the extension tube180. This wall plate 185 is supplemented by an outer triangular wallplate 186 which is pivoted in reverse relationship to the innerwallplate 185. That is to say, the outer wall plate 186 has a rearwardlyextending apex which is pivoted to the inner wall plate 185 adjacent tothe rear edge of the latter on a transverse pivot pin 187. Formed in theouter wall plate 186 adjacent to its swinging front edge is a longarcuate slot 188, and passing through this slot and through the loweredge of the inner wall plate 185 is a clamping bolt 189 which serves toclamp the outer wall plate to the inner Wall plate in different anglesof adjustment. A handle 191 secured to the upper portionof the outerwall plate 186 facilitates raising andlowering the outer wall plate 186into these different angles of inclination, in which it is held by theclamping bolt 189. For example, when the strike-off box 175 is in a lowposition of adjustment for filling a deep trench T, as indicated inFIGURE 5, the outer Wall plate 186 is also adjusted into a lowerposition, with its bottom edge 186' extending substantially horizontaland parallel with the bottom of the trench T. On the other hand, whenthe machine is traveling along the road in transport condition, or isonly filling a relatively shallow trench T, with the inner wall plate185 tilted up to an elevated position, the outer wall plate 186 is thenlikewise tilted up to an elevated position with the clamping bolt 189tightened in a lower portion of the arcuate slot 188, thereby insuringthat both wall plates occupy an elevated position.

The rear wall 177 of the box is secured to the rear vertical edge of thetriangular wall plate 186. As shown in FIGURE 2, this rear Wall 177 ismade up of one or more vertically extending fabricated steel sections177a, 177b, 1770, etc., which are adapted to be releasably securedtogether and to the triangular wall plate 185 by transverse bolts 193.The strike-off width of the box 175 can be increased or decreased by theaddition or removal of successive rear wall sections 1770, 177d, etc.;and concurrently with the addition or removal of these sections thefront extension tube 180 is shifted outwardly or inwardly to bringdifferent arcuate notches 181 into registration with the latching pin182. The lower front edge of each wall section 177a, 177b, etc. is facedwith a reenforcing or wear resisting bar 194 (FIGURE 5). Projectingrearwardly from the back of one of the rear wall sections, such as thesection 1770, is a pivot lug 195 carrying a pivot pin 196. Engaging overthis pin is a clevis 197 at the lower end of the piston rod 198 of thedouble acting hydraulic ram 176. The cylinder 199 of this hydraulic ramhas a clevis 201 at its upper end which is pivotally connected by pin202 with a tongue 203 extending downwardly from the outer end of anoverhead support tube 204. This support tube 204 extends horizontallyacross the top of the machine frame, where it passes through two spacedclamping brackets 285. Each of these clamping brackets has upwardlyprojecting yoke halves 206 which are adapted to be drawn together intorigid clamping engagement over the support tube 204 by the tightening oftransverse clamping bolts 208. By releasing the clamping bolts 208, thesupport tube 204 can he slid inwardly or outwardly in order to maintainthe double acting ram 199 substantially vertical as rear wall sections177b177d, etc. are added or removed to vary the strike-off width of thestrike-off box 175.

Bolted or otherwise secured to the inner side of the innermost wallsection 177a is a vertical movable guide plate 211 (FIGURE 5) whichextends substantially the height of the wall section and which has itsfront edge 212 curved in the form of an arcuate concave guide surface,and which has its rear edge 213 curved in the form of an arcuate convexguide surface, both of which curved guide surfaces have the pivotalcenter x of the extension tube 180 as their center of curvature. Thefront concave arcuate guide surface 212 has sliding guided engagementwith a stationary convex arcuate guide surface 214 of correspondingradius formed along the back edge of a stationary vertical guide plate215 which is secured to the adjacent side of the machine. Thisstationary guide plate 215 has its bottom horizontal edge 215terminating substantially at the hinged trench and curb seal 217, whichwill be presently described. The matching engagement of the two arcuateguide surfaces 212-214 in the different raised and lowered positions ofthe strike-oif box prevents any of the fill material from workinginwardly across the face of the rear wall 177 and discharging beyond theinner edge of this rear wall.

Referring now to the rear convex guide surface 213 on the guide plate211, the strike-olf box 175 is laterally restrained against any inwardor outward motion which would tend to laterally separate the arcuateguide surfaces 212-214, this lateral restraint being effected by thecoaction between said rear convex guide surface 213 and a restrainingroller 220 which rides on said guide surface (FIGURE 11). Thisrestraining roller 220 has an outer annular flange 222 which overlapsthe outer surface of the movable guide plate 211 along the convex rearguide surface 213. The restraining roller 220 is pivotally mounted on apivot pin 223 projecting outwardly from a stationary mounting bar 224which is secured to the frame of the machine directly on the inner sideof the movable guide plate 211. This mounting bar 224 restrains inwardshifting movement of the guide plate 211, and the outer confining flange222 of the roller 220 restrains outward shifting movement of the movableguide plate 211, whereby inward or outward displacementof the strike-offbox 175 is positively prevented. A reenforcing stationary strut bar 225may extend between the mounting bar 224 and the machine frame.

Referring now to the hinged trench and curb seal 217, it will be seenfrom FIGURES 9 and 10 that this seal extends horizontally directly belowthe large discharge opening 162 through which the fill material isdischmged from the conveyor belt 132. This seal 217 comprises alonghinge leaf 230 having hinge eyes 231 in alignment

